WO1990014528A1 - Cellule de charge a double piston - Google Patents

Cellule de charge a double piston Download PDF

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Publication number
WO1990014528A1
WO1990014528A1 PCT/US1990/003107 US9003107W WO9014528A1 WO 1990014528 A1 WO1990014528 A1 WO 1990014528A1 US 9003107 W US9003107 W US 9003107W WO 9014528 A1 WO9014528 A1 WO 9014528A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
chamber
wall
load cell
cylinder
Prior art date
Application number
PCT/US1990/003107
Other languages
English (en)
Inventor
John M. Montague
Original Assignee
Regal International, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Regal International, Inc. filed Critical Regal International, Inc.
Publication of WO1990014528A1 publication Critical patent/WO1990014528A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/20—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper characterised by comprising also a pneumatic spring
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02B—HYDRAULIC ENGINEERING
    • E02B3/00—Engineering works in connection with control or use of streams, rivers, coasts, or other marine sites; Sealings or joints for engineering works in general
    • E02B3/20—Equipment for shipping on coasts, in harbours or on other fixed marine structures, e.g. bollards
    • E02B3/26—Fenders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
    • F16F9/08—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid where gas is in a chamber with a flexible wall
    • F16F9/096—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid where gas is in a chamber with a flexible wall comprising a hydropneumatic accumulator of the membrane type provided on the upper or the lower end of a damper or separately from or laterally on the damper
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/30—Adapting or protecting infrastructure or their operation in transportation, e.g. on roads, waterways or railways

Definitions

  • the invention relates to a double piston load cell in which a resilient cup is bonded to the inner wall of a cylinder and outer walls of the pistons to form a chamber charged with pressurized fluid to ad ⁇ just the spring rate of the load cell.
  • Hydraulic cylinders have been connected to a hydraulic accumulator and used as a spring for various applications.
  • sliding seals between the pis ⁇ ton and cylinder wall may leak at high hydraulic pres ⁇ sures and may wear as a result of oscillating loads being applied to the piston.
  • shock cells mounted between a bumper and an offshore platform to absorb shock transmitted to the platform during boat landings and the like.
  • the shock cells incorporate a cylindrical rubber body adhered to the inner surface of a stationary supporting cylinder and to the outer surface of a movable cylinder telescopi- cally disposed in the stationary cylinder such that the cylindrical rubber body dissipates major compo ⁇ nents of shock applied to the movable inner cylinder.
  • the cylinders were sealed to prevent entry of sea water and other corrosive material.
  • Shock cells of the type disclosed in the afore ⁇ mentioned patents offered significant improvements over structures previously used and have enjoyed sig ⁇ nificant commercial success for the disclosed applica ⁇ tion.
  • the stiffness or "spring rate" of the shock cell was fixed when the shock cell was con ⁇ structed and could not be readily changed without extensive modification of the structure.
  • the double piston load cell disclosed herein includes at least one piston telescopically disposed in a cylinder.
  • a rubber cup is bonded to the outer surface of the piston and to the inner surface of the cylinder to form an enclosed chamber.
  • a source of pressurized compressible fluid such as air or nitrogen communicates with the enclosed chamber. Piston dis ⁇ placement, resulting from loads applied to the piston, deforms the rubber cup and compresses the compressible fluid. Adjustment of the volume of the compressible fluid adjusts the "spring rate" of the load cell.
  • the chamber in the load cell is preferably charged with a quantity of compressible fluid and a quantity of incompressible material, the volume of incompressible material being adjustable to control the volume and pressure of the compressible fluid over a predetermined range of piston displacement when predetermined forces are applied to the piston.
  • the pressurized fluid may be injected directly into the chamber or may be enclosed in an external hydraulic accumulator.
  • Physical dimensions of the load cell depends on the magnitude of force to be applied. Cells for some applications may require a piston displacement of from one to four inches when forces of from 1,000 to 2,000 pounds are applied.
  • the cylinder of the load cell may be 36 inches in diameter and nine to ten feet long. Loading on the pistons may be in a range of several hundred tons while pressure in the cylinder is in a range of, for example, three hundred to one thousand pounds per square inch. The combined displacement of the two pistons may be, for example, 40 inches.
  • the resilient cups bonded between the piston and the cylinder body of the load cell permit limited movement of the pistons relative to the cylindrical load cell body.
  • sliding seals typically employed in hydraulic cylinders have been eliminated.
  • Incompressible liquid or solid material can be pumped into the cylinder for adjusting the volume occupied by the compressible gas to thereby adjust the spring rate of the load cell.
  • the spring rate of the load cell is determined by the length of the resilient cups bonded between the pistons and the cylinder, the pressure of the gas in the chamber between the pistons and the relative volumes occupied by the pressurized gas at various piston displacements.
  • Figure 1 is a partially sectionalized view of a first embodiment of the load cell, the pistons being in an extended position;
  • Figure 2 is a partially sectionalized view simi ⁇ lar to Figure 1, the pistons being displaced inwardly of the cylinder;
  • Figure 3 is a partially sectionalized view of a second embodiment of the load cell diagrammatically connected to a hydraulic system for adjusting pressure of fluid in the load cell;
  • Figure 4 is a partially sectionalized view of the second embodiment of the load cell, pistons being displaced inwardly of the load cell body;
  • Figure 5 is a graph illustrating magnitudes of force exerted on pistons in the load cell resulting from distortion of material in the cup walls and com ⁇ pression of a controlled volume of gas.
  • Numeral references are employed to designate like parts throughout the various figures of the drawing. DESCRIPTION OF PREFERRED EMBODIMENTS Referring to Figure 1 of the drawing, the numeral 10 generally designates a double piston load cell com- prising a cylindrical body 12 having an internal cham ⁇ ber 15, and a pair of pistons 20 and 30 extending into opposite ends of chamber 15.
  • the cylindrical body 12 has an inner cylinder wall 14 and an outer cylinder wall 16 encircling chamber 15.
  • Pistons 20 and 30 have outer piston walls 22 and
  • Plates 26 and 36 are welded or otherwise secured to outer ends of pistons 20 and 30 while face plates 27 and 37 are secured to inner ends of pistons 20 and 30 forming chambers 25 and 35, respectively, in pistons 20 and 30.
  • connectors 29 and 39 are welded or otherwise secured to plates 26 and 36, respectively, for connecting pistons 20 and 30 between any suitable members (not shown) for control- ling the relative movement of the members.
  • Face plate 27 on piston 20 has a passage 28 ex ⁇ tending therethrough such that chamber 15 and cavity 25 are in fluid communication.
  • face plate 37 on piston 30 is not perfo- rated.
  • a passage similar to passage 28 in face plate 27 may be formed through face plate 37, if it is deemed expedient to do so such that cavity 15 and chambers 25 and 35 are in fluid communication.
  • cups 50 having outer cylindrical surfaces 52 and inner cylindrical surfaces 54 are mounted in the annulus between the outer surface 22 of piston 20, the outer surface 32 of piston 30 and the inner wall 16 of cy ⁇ lindrical body 12.
  • the inner cylinder wall 14 adjacent opposite ends of cylindrical body 12 as well as outer surfaces 22 and 32 of pistons 20 and 30 are preferably shot blasted and cleaned with a solvent and then bonded to cup 50, as illustrated in the drawing.
  • the inner cylindrical surface 54 of cup 50 is bonded to the outer surface 22 of the tube forming piston 20 while the outer cylindrical surface of cup member 50 is bonded to the inner cylinder wall 14.
  • Cup 50 is simi ⁇ larly mounted on piston 30.
  • end surfaces 56 and 58 on cup members 50 are inclined, arcuate end surface 56 being generally coni ⁇ cal in shape to form a projection extending outwardly from one end of cup 50.
  • End surface 58 on the oppo ⁇ site end of cup 50 is conical shaped to form a tapered recess in the inner end of cup 50.
  • an axially applied load "F" to pistons 20 and 30 deforms the wall of each cup 50 as the pistons move from the position illustrated in Figure 1 of the draw- ing to the position illustrated in Figure 2.
  • a second embodiment of the load cell is generally designated by the numeral 80 in Figures 3 and 4 of the drawing.
  • the second embodiment is substantially iden ⁇ tical to the structure hereinbefore described in ref- erence to the first embodiment except that a guide sleeve 82, having perforations 84 formed in the wall thereof, extends into opposite ends of the tubular members forming pistons 20 and 30.
  • face plates 27 and 37 have been omitted and that guide sleeve 82 is telescopically disposed in cavities 25 and 35 of pistons 20 and 30.
  • Guide sleeve 82 main ⁇ tains pistons 20 and 30 axially aligned even under lateral loading.
  • Chamber 15 is in fluid communication with cavities 25 and 35 through perforations 84 and the central passage 85 through guide sleeve 82.
  • the stiffness of load cells 10 and 80 may be adjusted by selecting cups 50 having varying lengths which results in varying the volume of rubber or other resilient material which is compressed when pistons 20 and 30 are urged inwardly.
  • a volume of pressurized compressible fluid 70 may be deposited in chamber 15 such that the pressure of fluid 70 is increased as the volume of chamber 15 is reduced as pistons 20 and 30 are displaced inwardly.
  • the volume of fluid in load cell 10 can be increased by forming a passage 28 in face plate 27 on the end of piston 20 and further increased by forming a second passage through face plate 37 on piston 30.
  • Fill pipes 65 and 75 having passages extending therethrough are welded or otherwise secured to the wall of body member 12 and to the wall of tube 20. Passages through fill pipes 65 and 75 may be closed with threaded plugs or equipped with suitable valves 62 and 72 through which pressurized gas, solid materi- al or liquid may be introduced to provide a desired initial pressure in chamber 15 and to adjust the vol ⁇ ume in the chamber occupied by the gas.
  • the stiffness of load cell 10 is further adjust ⁇ able by depositing a quantity of incompressible mate- rial, such as liquid 60, having a surface 61, in cham ⁇ ber 15 in addition to the volume 70 of compressible fluid.
  • the incompressible fluid 60 preferably com ⁇ prises mineral oil or other inert material while the compressible fluid 70 preferably comprises nitrogen gas. It should be readily apparent that when incom- pressible liquid 60 is introduced into chamber 15, the volume of the chamber filled with compressible fluid 70 is reduced, compressible liquid 60 displacing the compressible gas 70. It should be appreciated that shot pellets or other solid material may be deposited in chamber 15 to reduce the volume which is occupied by gas.
  • an external accumula ⁇ tor may be employed in combination with a pump for delivering pressurized fluid into cavity 15.
  • the pressurized fluid may be delivered through fill pipe
  • incom ⁇ pressible liquid 60 or compressible gas 70 may be introduced into chamber 15 or removed therefrom for adjusting pressure in chamber 15 and consequently the force required for movement of pistons 20 and 30.
  • a hydraulic line 100 is connected between fill pipe 65 and hydraulic pump 105.
  • Pump 105 is connected through suitable hydraulic lines to deliver incompressible liquid, such as mineral oil, from a reservoir 110 into chamber 15 in the cylindrical body 12.
  • a conventional external bag-type hydraulic accumulator 120 is con ⁇ nected to hydraulic line 100.
  • the bag type accumula- tor 120 includes a closed cylinder 122 containing a rubber bag 124 filled with air or gas.
  • Hydraulic fluid 125 is pumped into cylinder 122 under pressure, compressing the gas in the bag 124.
  • a release valve 126 is connected to hydraulic line 100. When the release valve 126 is opened, gas pressure in bag 124 forces hydraulic fluid 125 from the cylinder into hydraulic line 100.
  • Valve 130 in line 132 which is connected to hydraulic line 100, can be selectively opened for reducing pressure in the load cell.
  • the end points A and B on the upper straight line curve graph ⁇ ically illustrate design criteria for a typical load cell.
  • the lower curve containing points C and D graphically represents force exerted by a cup 50 to resist displacement of piston 20 relative to cylinder body 12.
  • the load cell is preferably tested to determine whether or not the specified loading and displacement requirements are met.
  • the graphically illustrated data indicates that when chamber 15 is vented to atmosphere a force of only 400 pounds displaced piston 20 one inch.
  • pressurized air, nitrogen or other gas is delivered through valve 17 and fill pipe 75 to exert sufficient force on piston 20 to support an applied load of 1,000 pounds at a deflection of one inch.
  • 400 pounds of force would be required to deform cup 50 while 600 pounds of force would be exerted by the compressed gas 70 to support the applied load of 1,000 pounds.
  • the increase in pressure of gas 70 in chamber 15 is related to the volume of air occupying all or a portion of chamber 15.
  • the force required for dis ⁇ placing the piston one inch is less than the force required to displace the piston one inch to compress a smaller volume of gas.
  • solid material such as metallic spheres may be introduced through fill pipe 65 for adjusting the volume of chamber 15 in lieu of liquid, if it is deem ⁇ ed expedient to do so.
  • the volume of chamber 15 may be adjusted by in ⁇ troducing incompressible material into the chamber either before or after pressurized gas is delivered into chamber 15 for adjusting the deflection of the load cell to reach point A on the curve illustrated in Figure 5 when the specified load is applied.
  • a family of curves AB may be generated by adjusting the proportion of the volumes of incompressible material and com ⁇ pressible material in load cells 10 and 80 to adjust the stiffness or "spring rate" of the load cells.
  • valves 62 and 72 may also function as bleed valves for removing gas or liquid from the system through one valve while gas or liquid is introduced through the other valve to adjust the proportion of the volume of incompressible materi ⁇ al to the volume of gas.
  • the ratio in the change in volumes of gas compressed as piston 20 moves from the position illustrated in Figure 1 of the drawing ' to the position illustrated in Figure 2 of the drawing can be precisely controlled and adjusted.
  • the total volume available to be occupied by gas can be adjusted to establish the correct mathematical ratio of pres ⁇ sure to volume required to cause load cell 10 to per ⁇ form in accordance with the specifications graphically illustrated in Figure 5.
  • the double piston load cell 10 comprises a cy ⁇ lindrical body 12 and a pair of tubular pistons 20 and 30 having cups 50 bonded to outer cylindrical walls 22 and 32 of pistons 20 and 30 and to inner wall 24 of cylindrical body 12 to form an enclosed vessel having chamber 15 disposed therein.
  • Force required for mov ⁇ ing pistons 20 and 30 into cylindrical body 12 can be adjusted by adjusting the pressure of compressible fluid 70 in chamber 15.
  • the volume of chamber 15 occupied by compressible fluid 70 can be adjusted by introducing a volume of incompressible fluid 60 into chamber 15.
  • Gas 70 is bled from the chamber 15 and cavity 25 through fill pipe 75 to fill both the chamber 15 and cavity 25 with fluid 125 when accumulator 120 is em ⁇ ployed.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Environmental & Geological Engineering (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

Les cellules de charge utilisées à des pressions hydrauliques élevées sur leurs joints de piston, présentent des problèmes d'usure et de fuites. Par liaison d'un godet en caoutchouc entre le piston et le cylindre associé, on peut réduire lesdits problèmes. La structure comprend une cellule de charge (10) à double piston comportant un cylindre (12), une paire de pistons (20, 30), ainsi qu'un godet résilient compressible (50) lié à la paroi intérieure du cylindre (12), ainsi qu'à la paroi extérieure (22, 32) du piston (20, 30), afin de former une chambre fermée (15) dans ledit cylindre (12). Une quantité de liquide incompressible (70) se trouvant dans ladite chambre fermée (15) occupe un premier volume, et une quantité de gaz compressible se trouvant dans la chambre occupe un second volume. Un changement dans le volume du liquide incompressible (70) par rapport au second volume de gaz compressible, commande le déplacement des pistons lorsqu'une force prédéterminée est appliquée auxdits pistons (20, 30). Ladite cellule de charge trouve une utilisation en tant que structure d'amortissement ou d'atterrissage marine.
PCT/US1990/003107 1989-05-26 1990-05-25 Cellule de charge a double piston WO1990014528A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US35736189A 1989-05-26 1989-05-26
US357,361 1989-05-26

Publications (1)

Publication Number Publication Date
WO1990014528A1 true WO1990014528A1 (fr) 1990-11-29

Family

ID=23405269

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1990/003107 WO1990014528A1 (fr) 1989-05-26 1990-05-25 Cellule de charge a double piston

Country Status (1)

Country Link
WO (1) WO1990014528A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5299790A (en) * 1991-09-17 1994-04-05 Ltv Energy Products Co. Elastomeric strut for an elastomeric riser tensioner
WO1994025775A1 (fr) * 1993-04-27 1994-11-10 Strömsholmens Mekaniska Verkstad Ab Agencement d'un ressort utilisant un gaz
US5482406A (en) * 1993-04-15 1996-01-09 Continental Emsco Company Variable spring rate compression element and riser tensioner system using the same
US5641248A (en) * 1993-04-15 1997-06-24 Continental Emsco Company Variable spring rate compression element and riser tensioner system using the same
WO2012030761A3 (fr) * 2010-08-31 2012-09-20 Oshkosh Corporation Ensemble ressort à gaz pour un système de suspension de véhicule
US10221055B2 (en) 2016-04-08 2019-03-05 Oshkosh Corporation Leveling system for lift device

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2421585A (en) * 1944-12-13 1947-06-03 Gen Tire & Rubber Co Fluid-modified mounting
US4352487A (en) * 1980-11-18 1982-10-05 Gould Inc. Viscous spring damper
JPS5999133A (ja) * 1982-11-30 1984-06-07 Toyoda Gosei Co Ltd 液封入防振装置
US4603843A (en) * 1983-04-22 1986-08-05 Caoutchouc Manufacture Et Plastiques Rubber mount with elastic control
JPS61218845A (ja) * 1985-03-22 1986-09-29 Nissan Motor Co Ltd 流体入りマウント装置
US4700933A (en) * 1983-03-15 1987-10-20 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Shock absorbing apparatus for an engine
US4784378A (en) * 1985-11-14 1988-11-15 Ford Motor Company Vibrating body mounting assembly

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2421585A (en) * 1944-12-13 1947-06-03 Gen Tire & Rubber Co Fluid-modified mounting
US4352487A (en) * 1980-11-18 1982-10-05 Gould Inc. Viscous spring damper
JPS5999133A (ja) * 1982-11-30 1984-06-07 Toyoda Gosei Co Ltd 液封入防振装置
US4700933A (en) * 1983-03-15 1987-10-20 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Shock absorbing apparatus for an engine
US4603843A (en) * 1983-04-22 1986-08-05 Caoutchouc Manufacture Et Plastiques Rubber mount with elastic control
JPS61218845A (ja) * 1985-03-22 1986-09-29 Nissan Motor Co Ltd 流体入りマウント装置
US4784378A (en) * 1985-11-14 1988-11-15 Ford Motor Company Vibrating body mounting assembly

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5299790A (en) * 1991-09-17 1994-04-05 Ltv Energy Products Co. Elastomeric strut for an elastomeric riser tensioner
US5433423A (en) * 1991-09-17 1995-07-18 Continental Emsco Company Elastomeric strut for an elastomeric riser tensioner
US5482406A (en) * 1993-04-15 1996-01-09 Continental Emsco Company Variable spring rate compression element and riser tensioner system using the same
US5641248A (en) * 1993-04-15 1997-06-24 Continental Emsco Company Variable spring rate compression element and riser tensioner system using the same
WO1994025775A1 (fr) * 1993-04-27 1994-11-10 Strömsholmens Mekaniska Verkstad Ab Agencement d'un ressort utilisant un gaz
US5580032A (en) * 1993-04-27 1996-12-03 Stromsholmens Mekaniska Verkstad Ab Arrangement for a gas spring
US8764029B2 (en) 2010-08-31 2014-07-01 Oshkosh Corporation Gas spring assembly for a vehicle suspension system
US8465025B2 (en) 2010-08-31 2013-06-18 Oshkosh Corporation Gas spring assembly for a vehicle suspension
WO2012030761A3 (fr) * 2010-08-31 2012-09-20 Oshkosh Corporation Ensemble ressort à gaz pour un système de suspension de véhicule
US8991834B2 (en) 2010-08-31 2015-03-31 Oshkosh Defense, Llc Gas spring assembly for a vehicle suspension system
US9688112B2 (en) 2010-08-31 2017-06-27 Oshkosh Defense, Llc Gas spring assembly for a vehicle suspension system
US10421332B2 (en) 2010-08-31 2019-09-24 Oshkosh Defense, Llc Gas spring assembly for a vehicle suspension system
US11225119B2 (en) 2010-08-31 2022-01-18 Oshkosh Defense, Llc Gas spring assembly for a vehicle suspension system
US11225120B2 (en) 2010-08-31 2022-01-18 Oshkosh Defense, Llc Gas spring assembly for a vehicle suspension system
US10221055B2 (en) 2016-04-08 2019-03-05 Oshkosh Corporation Leveling system for lift device
US10934145B2 (en) 2016-04-08 2021-03-02 Oshkosh Corporation Leveling system for lift device
US11565920B2 (en) 2016-04-08 2023-01-31 Oshkosh Corporation Leveling system for lift device
US11679967B2 (en) 2016-04-08 2023-06-20 Oshkosh Corporation Leveling system for lift device

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